engstrom



[- ENGSTROM ADDING MACHINE Feb. 20, 1951 7 Sheets-Sheet 1 Filed March 31, 1949 INVENTOR. IVAN ENGSTROM BY M ATTORN EY.

Feb. 20, 1951 l. NGsTRoM 2,542,403

ADDING MACHINE Filed March :51, 1949 7 sheets-sheet s IN VEN TOR. 58

ATTORNEY.

Feb. 20, 1951 l. ENGSTROM 2,542,403

ADDING MACHINE Filed March 31, 1949 7 Sheets-Sheet 4 INVENTOR. IVAN ENGS "mom Maxi/Me ATTORNEY.

1. ENGSTROM ADDING MACHINE Feb. 20, 1951 '7 Sheets-Sheet 5 Filed March 31, 1949 INVENTOR. IVAN ENGSTROM.

ATTORNEY Feb. 20, 1951 l. ENGSTROM 2,542,403

ADDING IACHINE Filed March 31, 1949 7 Sheets-Sheet 6 INVENTOR. IVAN- ENGSTROM ATTORNEY Feb. 20, 1951 1. ENGSTROM 2,542,403

ADDING-MACHINE Filed March 31, 1949 7 Sheets-Sheet 7 INVENTOR. IVAN ENGSTROM ATTORNEY Patented Feb. 20, 1951 UNITED STATES PATENT OFFICE ADDING MACHINE Ivan Engstrom, Chicago, Ill.; Dorothy Engstrom administratrix of said Ivan Engstrom, deceased Application March 31, 1949, Serial No. 84,711

Claims. 1

It is an object of the invention to produce an adding machine including a keyboard for setting up in ordered arrangement numerical items to be summated, and mechanism for transferring said items successively to totalizing devices affording a. visual indication of the sum or total of said items and by the same operation clearing the keyboard of each set-up item and restoring said keyboard to its initial or zero condition by each said transfer, and including also means for clearing said totalizing devices and restoring them to initial or zero condition at the will of the operator after each complete totalizing operation has served its purpose, and effecting all of said operations by novel mechanism and with a degree of accuracy and reliability not attainable with heretofore proposed adding machines for reasons below set forth.

The machine of the invention has a keyboard 01' the sector type, ordered and angularly movable sectors being employed in the set-up mechanism, said sectors having radially extending fingers which together with stationary digit indicators constitute the keyboard of the machine, a spring detent being provided for each sector to yieldingly hold it in any set-up position to which it may be moved. The machine employs ordered totalizer wheels axially aligned and carrying printed or embossed numerical figures readable through a sight opening or openings in the machine casing to give an indication of the total amount of operation of the totalizer Wheels; said totalizer wheels are respectively provided with attached ratchet wheels of novel construction below described, which ratchet wheels respectively include side Walls, each having formed therein or therethrough equally spaced clutch openings in a circular arrangement coaxial with the ratchet wheel, which openings are the same in number as the number of indicating figures or numerals on the corresponding totalizer wheel.

Each of the set-up sectors carries or has formed on its edge, gear teeth of a segmental gear, meshing at all times with the teeth of an idler gear, which idler gear has its teeth at all times in mesh also with the teeth of a transfer gear supported for independent rotation on the shaft supporting the totalized wheels. Each transfer gear is movable axially on the shaft supporting it, for clutching purposes, and carries a clutch pin in radial alignment with the clutch openings in an adjacent one of the totalizer ratchet wheels, each of said transfer gears being mounted on its supporting shaft adjacent one of said totalizer ratchet wheels and movable towards and from said ratchet wheel to engage and disengage its clutch pin with an opening or hole in the ratchet wheel determined by the angular position the corresponding totalizer wheel may then have on its supporting shaft.

The machine of the invention is provided with a handle or crank for operation after each keyboard set-up is eilected, and cam devices operated by said handle effect the operations below described.

It will be noted that operating the set-up fingers to set up a desired item on the keyboard, serves only to impart angular movement to the sectors, to the idler gears and to the transfer gears, the latter then being in positions entirely disengaging their clutch pins from the totalizer ratchet wheels. It is also to be noted that spring detents are provided for the totalizer wheels, each engaging one of said totalizer ratchet wheels and tending to hold the corresponding totalizer wheel in its position of last operation. The totalizer detents and the sector detents are so related that for any selected position of any sector in effecting any keyboard set-up, the clutch pin of the corresponding transfer gear is in alignment with one of the clutch openings in the adjacent totalizer ratchet wheel.

Thus, there being no operating connection of any kind between the sectors and the totalizer wheels during a keyboard set-up operation, when any said set-up is being made the operator may change it in any manner he pleases, without in any way affecting the totalizer Wheels, the final set-up amount on the keyboard immediately preceding a transfer operation, being the only amount that can then be transferred to the totalizer wheels.

The operating handle of the machine when at rest is preferably in a back position away from the operator, and a complete cycle of operation of said handle includes a complete forward movement of said handle and then a complete back stroke thereof. In view of it being important to the successful operation of the machine that the forward movement of the handle be complete before its back movement is begun, and that, once begun, the back movement of the handle shall be complete, a full-stroke mechanism as below described is employed to insure movement of the handle through its entire cycle of operation, whenever said handle is given any forward movement from its back position.

After a desired keyboard set-up has been established, movement of the operating handle from its back position as far as the transfer operation is concerned, first, by the cam devices referred to, moves all of the clutch pins so that they enter the openings in the totalizer ratchet wheels with which they are in alignment. This, because of the positive gearing of the sectors to the transfer gears, and because of the positive clutch engagement between the transfer gears and the ratchet wheels rigidly connected with the totalizer wheels, establishes for the time of transfer, apositive and unyielding train of mechanism between each sector and the corresponding totalizer wheel; during the transfer, any and all movement of each sector is accurately reflected in movement of the corresponding totalizer wheel, and it is impossible for any totalizer wheel to have any movement not imparted to it by movement'of the corresponding sector.

Continued forward movement of 'the operating handle maintains the positive clutch engagement referred to, and by said cam devices operates a sector returning shaft having radially extending arms rigidly carried thereby which engage studs on the sectors and move the latter back towards their zero positions. The returning movement of each sector begins at a, point in the movement of its returning arm determined by the amount of forward movement previously given the sector in establishing the set-up being transferred, and ends when the sector reaches a fixed stop determining its zero position; the returning or back movement of each sector thus effected, advances the totalizer wheel then positively clutched to the corresponding transfer gear which in turn is positively geared to the sector, the sante number of units as required to move the sector back to its zero position, or differently stated, the units represented by the set-up of the sector are positively and accurately transferred to the totalizer wheel, there is no possibility of slippage during the transfer movement and the totalizer wheel must advance the same number of units as the units of set-up of the sector, and the totalizer wheel cannot have greater angular movement than the movement given it by resetting the sector to its zero position, and the possibility of overthrow of the totalizer wheel is avoided, regardless of the rapidity of movement of the operating handle. Adding machines have heretofore commonly employed pawl and ratchet mechanisms for operating their totalizer wheels, and overthrow with such machines has frequently occurred, coupled with inaccurate indicationsof totals, a result impossible with the present invention.

After the forward movement of the operating handle has reset the sectors to their zero positions, and said totalizer wheels are at rest and under the control of their spring detents, the operating handle has a small remaining amount of forward movement which by said cam devices, moves said transfer gears away from the adjacent totalizer ratchet wheels a sufficient distance to move the clutch pins from engagement with said ratchet wheels, thereby freeing said sectors for the next set-up operation.

It is a further object of the invention to reduce the load on the operating handle during the sector resetting operation, as much as possible without sacrificing accuracy of operation and without making the machine unduly complicated. If no devices were employed to prevent it, the load on the handle would necessarily include the full resistance of the totalizer spring detents and of the sector spring detents, as well as of the spring employed to hold the handle in its back posi ion until it is desired .to effect a transfer operation.

4 The invention provides means for materially reducing said load on the operating handle as follows. The sector spring detents are all mounted on a common bar which at its ends is pivotally supported by the frame of the machine, so that it may be oscillated to move the sector engaging portions of the detents towards and from the sectors which are notched at their edges to cooperate with said detents. A toothed disk is :mounted for rotation on a fixed part of the machine, for operation by said cam devices. The disk is positioned relatively to a free edge of said mounting bar so that in a first operative position of said disk, the bar edge rests between any two adjacent teeth of said disk, at which time a relatively strong spring or springsconnected with said bar press the latter .firmly against ,said disk to in turn press the detents with maximum holding pressure against the sectors; and so that in a second operative position of said disk, the bar edge is in engagement with one of said adjacent teeth of said disk, to move the detents away from the sectors enough to either substantially reduce their sector holding action or to entirely eliminatesa-id holdingaction, as preferred. At the beginning of each transfer operation, the rotary disk is in its first position and the detents exert their full holding ,efiecten the sectors; when the operating handle has been moved forwardly enough to enter the clutch pins into the clutch openings in the totalizer ratchet wheels, means between said disk and said cam devices of the machine, begin the turning of said dis; from its first position to its second position, which movement to its second position is completed at the time the clutching operation is .completed and before resetting movementof the sectors is begun, and the disk is held in said second position by said cam devices during the entire sector resetting operation; when the resetting'operation has been completed and simultaneously with the operation disengaging the clutch pins from the totalizer ratchet wheels, said cam devices move said disk from its second position to its first position, thereby restoring the full effect of said sector detents, and placing the sectors in condition-for the next set-up operation.

It is a further object of the invention to produce a carry-over mechanism for the machine, of the delayed carry-over type, which by .a simple, effective and novel construction below described, first stores any carry-over required by any transfer operation, and then at the .end of each back movement of the operating handle, operates the totalizer wheels to accurately .and reliably add said carry-over to the total :indiceted'by said totalizer, thereby accurately indicating the total summation of the several set-up items transferred to the totalizer Wheels since the 'last re-setting or cleering thereof.

To effect said carry-over, the invention provides each totalizer wheel excepting the one of lowest order, with a carry-over slide having reciprocatory movement towards and from the associated totalizer wheel and having 'a spring-actuated pawl in line with the ratchet wheel attached thereto. Each slide cooperates with two latches, a first of which is a trigger latch engaging the slide and preventing its carry-over movement unles said latch is actuated by movement .of the totalizer wheel of next lower order from its 9 to its 0 position, and the second of which is a timing latch and restrains the slide against carry-over movement when said slide is released by said trigger latch, until just before the operating handle reaches the end :of its back stroke. The trigger latch is provided with an arm having an end lug extending through an opening in a partition of the machine between said trigger latch and the totalizer wheel of next lower order, which lug extends into the path of a cam carried by the last mentioned totalizer wheel in such a manner that when in any way the latter is rotated from its 9 position of indication to its 0 .position, its cam raises said arm and thus moves the triggerlatch enough to free the slide from restraint by said trigger latch, and an operating spring connected with the slide at once moves the latter forwardly towards the totalizer wheel cooperating with said slide, a small amount sufficient to prevent reestablishing holding engagement between said trigger latch and said slide when the lug of the latter latch is freed from the totalizer cam of next lower order, which occurs just before the totalizer wheel of next lower order reaches its 0 position; said small amount of forward movement of the slide is not enough to bring the pawl of the slide into engagement with its associated totalizer ratchet wheel, and is permitted by a corresponding amount of play between the timing latch and the portion of the slide engaged by it, said timing latch for the moment being the only mean restraining the slide from forward movement by its actuating spring to advance the associated totalizer wheel one unit; in its position of rest, said lug of the trigger latch rests on the lower edge of the opening in the partition through which it passes, and a second lug carried by said trigger latch lies in the path of forward movement of the slide and prevents forward movement of any kind under the action of its spring as long as that relation of parts continues, which is as long as there is no need for a carryover operation by the slide, and at that time, regardless of the position of the timing latch, the latter exercises no restraint against forward movement of the slide; when the arm of the trigger latch i raised by the totalizer cam of next lower order, the second lug of said latch is raised to entirely clear the slide, which permits instantaneous and entirely unrestrained forward movement of the slide the small amount referred to before such movement is stopped by the timing latch, as a result of which, when the first mentioned lug of said trigger latch is freed from the totalizer cam, the trigger latch, under the action of its returning spring, cannot then return to its position of rest, but, by the engagement of its second lug with an upper longitudinal surface of the slide is held in a somewhat raised position, which condition of the trigger latch continues through the carry-over operation and until the slide is moved to it extreme back position; the timing latch is provided with a spring holding it in its slide restraining position at all times excepting when the operating handle is in its extreme back position, means being provided on the operating shaft secured to said operating handle, by which the timing latch is moved to its slide releasing position during the last part of the back movement of the operating handle, which frees the slide, and the latter is then moved by its actuating spring through the remainder of its possible forward movement, by which its pawl engages the totalizer ratchet wheel and advances the totalizer wheel one unit and effects the necessary carry over. The means employed to move the timing latches of the machine to releasing or inoperative postiion at the end portion of the back stroke of the operating handle, also serve to free said timing latches during the first part of the forward movement of each cycle of operation of the operating handle, and at the same time or immediately thereafter, additional means controlled by the operating shaft move any of the slides that may then be in their forward positions a a result of effecting carry-over operations, to their rear positions and into holding engagement with said trigger latches with the timing latches in position to serve their holding purpose above described, which operations are completed before the transfer movement of the totalizer wheels above described, is begun by continued forward movement of the operating handle.

The carry-over operation may involve first, a single unit of advance for each totalizer wheel of next higher order than a totalizer wheel of lower order moved from its 9 position to or through it 0 position by a transfer operation; or second, a corresponding unit of advance for each of adjacent totalizer wheels of higher order initiated by movement of the totalizer wheel of the order next lower than the lowest of said totalizer wheels, where all of the totalizer wheels of higher order are in their 9 positions before the carry-over operation, in which case the carryover movement of said totalizer wheels is successive from lower to higher order, each of said totalizer wheels of higher order initiating in turn the carry-over movement of the totalizer wheel of next higher order.

further object of the invention is to provide the machine with means for resetting the totalizer wheels to their 0 positions when desired, which means includes devices preventing the re setting operation unless all of the carry-over slides are in their extreme back or retracted positions away from the totalizer wheels, to protect the carry-over pawls and totalizer ratchet wheels from damage that might occur if the pawls were not fully withdrawn and held so at the time of resetting, which retracted or back positions of the slides may readily be effected if a carry-over operation immediately preceded an attempted resetting operation, by an idle cycle of movement of the operating handle having no effect excepting to retract such of the slides as may then be in their carry-over positions. Said resetting means also includes devices for stopping the resetting movement of the totalizer wheels when they reach their 0 positions.

It is a further object of the invention to construct the parts of the machine by simple and inexpensive operations, such as punch press and screw-machine operations, and to so construct and relate the parts in the assembled machine, that close fits and small tolerances are avoided, thereby avoiding expensive workmanship and expense in assembling the machine, and all without sacrificing accuracy of operation and effectiveness in use, to the end that the entire cost of production may be relatively low and the demand for the machine may be large.

The above and other objects of the invention will more fully appear and be better understood by reference to the accompanying drawings illustrating a preferred embodiment of the invention, in which Fig. 1 is a side elevation of the complete adding machine to a reduced scale,

Fig. 2 is a front end elevation of the complete adding machine to a reduced scale,

Fig. 3 is a full-size plan view of the machine with the casing removed,

Fig. 4 is a vertical, sectional view of the struc- '7 ture shown in Fig. 3 taken along the line 4-4 in the latter figure,

Fig. 5 is a vertical, sectional view of the structure shown in Fig. 3 taken along the line 5-5 in the latter figure,

Fig. 6 is a view similar to Fig- 5 of a part of the structure therein, with the spring detent supporting bar in its alternate position.

Fig. '7 is a vertical, sectional view of the structure shown in Fig. 3 taken along the line 1-! in the latter figure, 1

Fig. 8 is a horizontal and inclined sectional view of the structure shown in Fig. 7 taken along the line 8-8 in the latter figure.

Fig. 9 is a View similar to Fig. 8 with the clutch members thereof and their operating devices in an alternate position,

Fig. 10 is a view similar to Fig. 8 with its clutch operating cam in its position of backward movement,

Fig. 11 is a vertical, sectional view of a part of the structure shown in Fig. 8 taken along the line II-il in the latter figure, and shows one of the transfer gears in front elevation,

Fig. 12 is an inclined sectional view of the gear shown in Fig. 11 taken along the line l2-l2 in the latter figure,

Fig. 13 is vertical sectional view of a part of the structure shown in Fig. 9 taken along the line I 3-l3 in the latter figure, and shows one of the totalizer ratchet wheels in front elevation,

Fig. 14 is a horizontal, sectional view of apart of the structure shown in Fig. 4 taken along the line I l-l4 in the latter figure and shows the main operating shafts of the machine.

Fig. 15 is an inclined sectional view of a part of the structure shown in Fig. 4 taken along the line I5-l5 in the latter figure, and. shows the clutch operating shaft and the shaft supporting the totalizer wheels and the transfer gears,

Fig. 16 is a vertical, axial, sectional view to an enlarged scale through one of the totalizer wheel assemblies,

Fig. 17 is a right hand and elevation of the structure shown in Fig. 16,

Fig. 18 shows in a view similar to Fig. 17, a right hand end elevation of the body portion of the totalizer wheel shown in Fig. 16, with the ratchet wheel, hub and internal plate and pawl removed,

Fig. 19 is a right hand end elevation of the wheel hub shown in Fig. 16,

Fig. 20 is a left hand end elevation of the internal plate and pawl shown in Fig. 16,

Fig. 21 is a vertical, sectional view of a part of the structure of Fig. 3 taken along the line 2 i-Zl in the latter figure, and shows the carry-over devices of the machine in side elevation with the carry-over slide in its fully retracted position,

Fig. 22 is a View similar to Fig. 21 and shows the trigger latch in its slide-releasing position, and the slide moved forwardly a small amount and still held by its timing latch,

Fig. 23 is a View similar to Figs. 21 and 22 and shows the timing latch withdrawn from slideholding engagement, and the slide in its carryover position,

Fig. 24 is a vertical, sectional view of a part of the structure shown in Fig. 3 taken along the line 24-24 in the latter figure, and shows a portion of the carry-over mechanism illustrated in Fig. 21, with the trigger latch in its position of rest and with the carry-over slide in the position shown in Fig. 21, 1

Fig.25 is a view-similar to Fig. 24 and shows the trigger latch in its fully raised position by the totalizer wheel of next lower order, the carryover slide being shown in this view in its position of slight forward movement'permitted by the timing latch in itsholding position as shown in Fig. 22,

Fig. 26 is a view similar to Figs. 24 and 25 and shows the totalizer wheel of next lower order in its 0 position releasing the trigger latch, and also shows the carry-over slide in its forward or carry-over position permitted by thereleasing position of the timing latch shown in Fig; 23

Fig. 27 is a vertical, sectional view of apart of the structure shown in Fig. 3 taken along the line 21-21 in the latter figure, and shows the means employed for controlling the resetting of the totalizer wheels, V

Fig. 28 is a vertical, sectional view of a part of the structure shown in Fig. 14 taken along the line 28-28 in the latter figure,

Fig. 29 is a vertical, sectional View of a part of the structure shown in Fig. 14 taken along the line 29-29 in the latter figure,

Fig. 30 shows in end elevation the inner end of the hub portion of the operating handle removed from the operatin shaft shown in Fig. 14,

Fig. 31 shows in right hand end elevation, the full stroke mechanism and hub portion of the operating handle employed in connection withthe operating shaft and shown in part in horizontal sectional view and in place on said shaft in Fig. 14,

Fig. 32 is a vertical, sectional view of the structure shown in Fig. 4, taken along the line 32-32 in the latter figure, i

Fig. 33 shows in a view similar to Fig. 32, 'a modified form of clutch mechanism between the transfer gear and the totalizer wheel shown in Fig. 32.

Figs. 34 and35 are vertical, sectional views of the structure shown in Fig. 33, taken respectively along the lines 34-34 and 35-35 inthe latter figure, i

Fig. 36 is a vertical, sectional view of a part of the structure shown in Fig. 3 taken along the line 36-36 in the latter figure, and

Fig. 3'7 is a vertical, sectional view to an enlarged scale, of a part of the structure shown in Fig. 1, taken along the line 31-31 in the latter figure. I

Similar numerals refer to similar parts throughout the several views. 7

The adding machine of the invention includes a framework comprising vertical, parallel and equally spaced partitions 2 to 8 inclusive (Fig. 3), of sheet metal, forming compartments -I to VI between them, and vertical end plates l and 9 of sheet metal parallel with and spaced from the adjacent partitions 2 and 8 respectively. Said partitions and end plates extend from front to rear of the machine, and are held together by tie rods in to M inclusive (Figs. 3, 4 and 36), extending through said partitions and end plates and carrying spacing sleeves l5 to I!) of metal between said partitions and end plates, by which said partitions and end plates are rigidly and se curely held together to constitute the framework of the machine, by end screws engaging said tie rods.

Each of the compartments I to VI contains a totalizer wheel 20 and attached ratchet wheel 2| and a transfer ear 22, which parts are mounted for rotary movement on a common supporting shaft 23 (Fig. 3), extending with a sliding fit through the partitions 2-8 inclusive; each of-said compartments also contains set-up devices including an oscillatory finger 24 adjacent a curved index plate 25 for setting up each amount to be transferred and added to the total Shown by the totalizer wheels said compartments I to VI inclusive thus correspond to the orders of units involved in the machine, being respectively from right to left of the machine, units, tens, hundreds, thousands, tens of thousands and hundreds of thousands, the capacity of the illustrative machine being 999,999.

Each of the compartments II to VI inclusive also contains carry-over mechanism of the delayed action type, including an operating slide 28, a trigger latch 21 and a timing latch 28 (Fig. 3), for advancing the totalizer wheel 20 of that order one unit as a result of the totalizer wheel of the next lower order bein rotated from its 9 to its 0 position. Many of the parts in the several compartments are duplicates of each other and are respectively referred to by the same reference numerals where confusion does not result from so doing; for example, the finger 24 may if unmodified, refer to said finger in any of the compartments, since the set-up mechanism in each compartment is the same as in each other compartment. If, however, for clarity, it is necessary to identify such a part in a particular compartment, for example, the finger 24 in compartment I, that effect is secured herein by designating said finger as finger 24-I. Similarly, where the carry-over operation in compartment II is discussed (Figs. 4, 21), the carry-over operation is initiated by totalizer wheel 2(l-I being turned from its 9 to its 0 position, which moves trigger latch 2'!-II from holding engagement with slide 26-II and transfers control of said slide, but not its complete release, to timing latch 28-II, which condition continues until just before the main operating handle 35 reaches the end of its operating cycle, at which time the timing latch 28II is moved from engagement with slide 26II and the latter under the action of its operating spring moves forwardly and advances the totalizer wheel 2fiII one unit or step, thus delaying the carry-over operation of the totalizer wheel 29II until the end of the operating cycle of the main handle 35.

As shown in l and 2, the machine is provided with a casing 29 of suitable material, for example, sheet metal or plastic, which has a front wall closely adjacent the index plates and totalizer Wheels which Wall is provided with a lower sight opening 39 disclosing all of the n"merical indications on the index plates 25, provided as an ad in effecting any desired set-up of the fingers 24 extending through said opening 39.

As shown in Figs. 2 and 3, each index plate 25 is prov ded with a s ght opening 3! disclosing an indcator 32 operated by the finger 24 and carrying digits showing at any t'me through said opening 3i 2. digit corresponding to the set-up position of said finger. and index pl es 25 together constitute the keyboard of the machine.

Above the si ht opening 30, the front wall of the casing 1'9 is provided with individual sight openings 33 extending across the casing and shot-.mg by means of numerals on the outer surfac s of the totaj' r wheels 29, the total value of de ired s .s of items or amounts succesr "elrecl to said wheels for correvol; trans: spen ing ite s of set-nu, and also showing after resetting said wheels following a desired sum- The fingers 25 mation, the 0 or cleared condition of said wheels. A resetting knob 34 having a hub extending through a clearance opening in the casing for connection with the rod 23, is provided to reset the wheels 29 to their 0 condition. A main operating handle 35 having a hub 35 extending through a clearance opening in the casing 29 for connection with the main operating shaft of the machine, is provided to effect after each set-up, a transfer of said set-up to the totalizer wheels 29, to clear the keyboard and restore the fingers 24 to their 0 positions, and to control the operation of the carry-over devices.

As shown in Fig. 37, the casing 29 fits closely around a base 37 to which it is secured by screws 38 as indicated. The base 31 is enough wider than the over-all width of the framework outside of the end plates 4 and 9, to support blocks or lugs 39 adjacent said end plates, which blocks are secured to the base by screws as as indicated. A front retaining rod 4i extends with a sliding fit through the blocks 39 and also through holes 42 therefor through the end plates 5 and 9 and through the partitions 2 to 8 inclusive to connect the framework with the base. A similar rod extends through similar blocks and also through the end plates and partitions to connect the rear portion of the framework with the base.

As shown in Fig. 14, the main operating shaft 43 of the machine is supported by end bearings 44 and 45 rigidly secured to the end plates 1 and 9. The shaft is of square cross-section excepting at its end portions, and carries arms 46 for in part controlling the carry-over mech-- an sm, and also cams 4'1, 48 and 49, which arms and cams have square holes that are a sliding fit on said shaft. Tubular metal spacers 59 and 5| having a square cross-section and a sliding fit on the shaft hold the arms and cams rigidly in place on the shaft. The spacer 59 is rigidly secured to the shaft by a pin 52 and is of a length from the round end of the shaft in the bearing 45 to hold the cam 4l' adjacent but sl ghtly spaced from the outer surface of the partition 8. The spacers 5! are unsecured to the shaft and are of lengths holding the cam 48 adjacent and slightly spaced from the right hand side of the partition 5 and holding the cam 49 a small distance to the right from the middle of the cornpartment I; said spacers 51 also hold the arms 46 in similar positions in the compartments II to VI inclusive, each in a position somewhat to the left of the middle of the compartment containing it. The shaft 43 extends with square cross-section a substantial distance to the right of the cam 49, and said square extension enters an end key-way 53 in a cylindrical connector 54, which keyway has a width closely fitting the opposite flat surfaces of said extens on and a depth somewhat greater than the length of said square extension. The right hand portion of the connector 54 is turned down and shouldered to turn freely in the bearing 44 and to prevent objectionable end play of the shaft in its bearings. Outside of its square extension, the shaft 43 is turned down to a diameter substantially equal to its dimension across its flat surfaces, and this cylindrical end portion 55 extends a substantial distance outside of the outer surface of the end wall I and is externally threaded. The outer end of the bearing 44 extends a small amount outside of the outer surface of the end wall 1, and the outer end of the cylindrical portion of the connector 54 is substantially flush with the outer end of the bearing 44. The connector 54 has a bore extending from its keyway 53 which closely fits the extension 55, and outside of its cylindrical end, said connector is provided with opposite end keys 56 closely fitting opposite keyways 51 in a full-stroke plate 58 mounted on the extension 55 '(Fig. 29). Between the keyways 51, the plate 58 is provided with a second pair of opposite keyways 59 fitting end keys 60 extending from the hub '36 of the handle 35. Fig. 28 is a left hand elevational view of the connector 54 removed from the shaft 43. In Fig. 29, the handle 35 is removed to more clearly show the keyways 59. Fig. 30 is a left hand elevational view of the handle hub 36 removed from the machine to more clearly show the end keys 60.

The hub 36 is provided with a bore substantially larger in diameter than the extension 55, to receive with a sliding fit a tubular extension 6| from a knurled head 62, which extension 6| is internally threaded to engage the external threads on the extension 55. The head 62 is shouldered as indicated and when screwed onto the extension 55, holds the hub 38 tightly against the plate 58 and also holds the plate 58 tightly against the end of the connector 54.

In assembling the shaft 43 and its parts, the spacer 59 is secured to the shaft by the pin 52, the spacers arms 48, and cams 41, 48 and 49 are placed on the shaft as indicated and described, and then the connector 54 is placed on the extension 55, and with the connector tightly pressed towards the spacer 50, a pin 63 is inserted through, the connector and through the shaft end in the keyway 53, thereby rigidly securing the arms 46 and the cams to the shaft. The lower right hand corners of the partitions 2 to 8 inclusive are cut away (Fig. 4), so that the shaft 43 and its parts may be assembled as a unit and then as such be placed in the bearings 44 and 45.

As also shown in Fig. 14, the machine is provided with a second square shaft 64 parallel with and in front of the shaft 43, and having turned ends for support by bearings 65 and 66 extending through and rigidly secured respectively to partitions 8 and 2. Sector resetting arms 67 spaced from each other and located respectively in compartments I to VI inclusive, and provided with square holes that are a sliding fit on the shaft 64, are mounted on said shaft, each in the right hand portion of the corresponding compartment, and said shaft also carries in the same manner, an operating arm 68 cooperating with the cam 49 (Fig. 4). The arms 67 and B8 are held in spaced relation by square tubular spacers 69 that are a sliding fit on the shaft 64. The right hand resetting arm 81 is held against movement to the right by a pin extending through the shaft 64 and against which pin said arm rests, and the arms and spacers are held in a tightly pressed condition against each other, by a pin H extending through the left hand spacer and also through the shaft 64. The lower portions of the partitions 3 to 1 inclusive are provided with clearance slots (Fig. 4), so the shaft 64 and its parts may first be assembled as a unit and then as such be placed in the bearings 65 and 66.

Fig. illustrates the assembly of totalizer wheels and ratchet wheels 2|, and transfer gears 22 on shaft 23, and also the clutch mechanism controlling the operation of the totalizer wheels by the transfer gears. Each totalizer wheel 20 and attached ratchet wheel 2| com'-' totalizer wheel and ratchet wheel combination,

a thin walled, tubular spacer 13 extending with a free fit axially, from the bushing 12 to the right hand partition of said compartment, to hold the totalizer wheel adjacent the left hand partition of said compartment. The transfer gear 22 in said compartment, is mounted on a grooved hub 14 having a bore that is a sliding fit on the spacer 13, said hub having a length axially permitting sufficient axial movement of the hub to the lefton the spacer '13, to move a clutch pin 75 carried by the transfer gear, into one of the holes I6 in the web of the ratchet wheel 2| with which said pin 15 may be in alignment, said ratchet .wheel thereby comprising the other member of the clutch mechanism. With the clutch members thus engaging each other, the totalizer wheel and ratchet wheel combination and the transfer gear are positively connected and must rotate as a unit, if rotary movement is imparted to any one of the parts of said unit, and there is no possibility of angular movement in either direction of any one of said parts relatively to any other one of the parts of said unit, and the extent of angular movement of any part of said unit cannot be different from the extent of angular movement of any other part of said unit. Axial movement of the *hub 14 to the right on the spacer I3, removes the clutch pin 15 from engagement with the ratchet wheel 2|, and at the same time provides a sufficient clearance space between said pin 15 and. said ratchet wheel to prevent accidental contact of the clutch pin with the ratchet wheel; for this open condition of the clutch mechanism, either the transfer gear 22 or the totalizer wheel and ratchet wheel combination may be freely rotated independently of the other, with no possibility of communicating rotary movement of any kind or amount to the other.

As shown in Fig. 15, the right hand end of the shaft 23 has rigidly secured to it between the end plate I and the partition 2 by a pin '18, a flanged control member 19 for the resetting operation of the totalizer wheels 29, which control member has a hub 88 extending through the end plate I and has a stepped end fitting the stepped inner end of a hub 8| extending from the resetting knob 34 with a slidin fit on the end portion of the shaft 23. A screw 82 threaded into the end of the shaft 23 holds the inner end of the hub 8| tightly against the hub 80, whereby resetting movement may be imparted to the shaft 23 by turning the knob 34, the knob 34 being readily removable from the shaft 23 for assembling and removing the casing 29, by removing the screw 82. The shaft 23 is provided with a small longitudinal keyway 83 extending through all of the totalizer wheels 20 to effect a resetting operation of said totalizer wheels by rotation of the knob 34.

As shown in Fig. 15, the groove in each of the hubs I4, is engaged by the forward end of a clutch operating plate 84 mounted at its rear portion on a square shaft 85 parallel with the shaft 23 and having turned end portions engaging with a sliding fit; bearings 86 and 81 rigidly supported by end wall 9 and partition 2 respectively. The plates 84 are provided with square holes that are sliding fits on the shaft 85, and said plates are held each in a similar position in the right hand portion of the compartment containing it, by square tubular spacers 88 on the shaft between said plates, which spacers and plates are held in a tightly pressed condition against each other by pins 89 extending through said shaft, thereby rigidly holding said plates in parallel spaced relation extending in the same direction from the shaft. A guide rod 90 extends with a sliding fit through the plates 84 and also through the partitions 2 to 8 inclusive but not through the end plates I and 9, the ends of said rod being adjacent the inner surfaces of said end plates to hold the rod in place without the use of fastening devices of any kind, which simplifies and cheapens the construction and also the assembly of the parts. The guide rod 90 prevents angular movement of the plates 86 and shaft 85 around the axis of said shaft, but permits free movement of said plates and shaft as a unit, axially of said shaft, which axial movement is employed to simultaneously move the clutch pins to their closed or clutching posit'ions in the holes 16, which movement is limited by engagement of the transfer gears 22 with the ratchet wheels 2|, and to simultaneously move the clutch pins 15 to their open or unclutched positions free from the holes 16, which movement is limited by engagement of the hubs M with the partitions 2 to l inclusive. The shaft '85 at its left hand portion is turned down and is a sliding fit in the partition 8 and outside of said partition is provided with an operating pin 9| extending through said shaft with its ends extending outside of said shaft, to impart axial movement to said shaft as below described. Outside of the pin 9|, the shaft 85 is shouldered and of reduced diameter through the bearing 85, a Washer 92 being carried by the shaft adjacent said shoulder, and between said washer and the bearing 86, a compression spring 93 is mounted around the shaft, which spring is of such strength as to positively move the shaft 85 to the right to its extreme unclutching position when the pin 9| is free from actuating force moving said shaft to the left to its clutching position. A clearance opening I2! is provided through each of the partitions 3 to inclusive around the shaft 85, permitting the mounting of said shaft in its bearings 86 and '87, after assembling the plates 84 on said shaft as described.

The totalizer wheels are preferably constructed as shown in enlarged scale views in Figs. 16 to 20 inclusive. Each of said wheels includes a unitary rim, web and hub structure of molded material, for example, metallic alloy or plastic, having a bore fitting the outer cylindrical sur face of a metallic bushing I2, said hub having in its right hand end a circular recess 94 having a fiat upper surface (Fig. 18), in which recess a flange 95 of similar form and size on the bushing I2 (Fig. 19), fits when the parts are assembled as shown in Fig. 16. The ratchet wheel 2| is of formed sheet metal having a web provided with a bore fitting the end portion of the bushing 12 just outside of the flange 95, so that the ratchet Wheel web and the bushing flange engage each other for the assembled condition of the wheel. The ratchet wheel web around its circular outer edge is provided with integral and equally spaced teeth, equal in number to the number of indicating digits carried by the rim of the totalizer wheel, for example ten teeth, there being ten equally spaced indicating digits shown herein as carried by said rim. although obvious y a multiple of that number may be employed if preferred; said teeth extend perpendicularly from the ratchet wheel web towards the web of the totalizer wheel, and at their left hand ends extend into shallow seats 96 therefor (Fig. 18), to afford stable support for said teeth ends when the parts are assembled as shown in Fig. 16. The ratchet wheel web is provided with equally spaced clutch holes '56 in a circular arrangement having the same radius as the radial distance of the axis of the clutch pins 15 (Fig. 15) from the axis of the shaft 23, said holes being the same in number as the number of indicating digits carried by the rim of the totalizer wheel, for example, ten of said holes (Fig. 1'7), for the illustrative structure shown in the drawings. Said holes are each of slightly larger diameter than the diameter of the clutch pins '15 cooperating therewith, and the outer ends of said pins are preferably rounded or chamfered to insure certain and easy entrance of said clutch pins into any of said holes with which they may be in alignment, during any clutching operation.

The inner wall of the web of the totalizer wheel 2-3 has resting against it and supports a metal disk 9' which is circular excepting for a cut-out portion S'la (Fig. 20). Said disl: has a bore fitting the bushing 12 and an external diameter slightly smaller than the inside diameter of the rim of the to'talizer wheel. Said disk 97 has pivotally secured thereto at 9%, a small pawl 89 having a pointed inner end projecting into the here in the disk and through a slot I00 therefor in the bushing '12 into the bore in said bushing, under the action of a tension spring l0! connecting the pawl with a lug 3-2 projecting from the disk, excepting when the inner end of said pawl is prevented from projecting into the bore in the bushing l2 by the shaft 23 in said bushing. The totalizer wheel 29, ratchet wheel 2!, bushing l2 and disk 9'! are held securely together in the assembled condition shown in Figs. 16 and 17 by rivets H33 extending through said parts. As a result of the structure described, with the structure of Figs. 1) and 17 mounted on the shaft 23, and viewing the structure from the left hand end of said shaft, the counter clockwise rotation of the totalizer wheels required. in totaling several items is freely permitted without angular movement of the shaft 23, whereas when it is desired to reset the totalizer wheels to their 9 condition, counter clockwise rotation of the shaft '23 in the manner below described, engages the pawls 96 in the keyway 83 in the shaft 23 and rotates all of the totalizer wheels not in their 0 condition, until they reach that condition. The cut out portion of the disk 91 is provided with a formed cam 194 extending perpendicularly therefrom to initiate carry-over operations as below descr bed.

As shown in Figs. 11 and 12, the clutch pin '15 is preferably a sliding t in a hole therefor in the transfer gear 22 and at its inner end is rigidly secured to the midportion of a flat arcuate spring 295 held under tension against the gear 22 by rivets Hi6 through the ends of said spring. The spring Hi5 holds the clutch pin '55 in the position shown in F. 12, nless by accident said is not in alignment with one of the clutch holes .76 in the ratchet wheel 2! (Fig. 13) when the transfer gear 22 is moved towai the ratchet wheel r? a clutching opera in which case the will yield and prevent damage to the parts that might otherwise occur.

In Figs. 33 to .35 inclusive, a modified construction of the clutching devices is shown, in which the clutch pin is carried by the ratchet wheel and the clutch holes are in the transfer gear, the construction being the reverse of that above described in connection with Fig. 15, but operating in an equivalent manner to produce the same results. In this modified construction, the totalizer wheel 20 is of the same construction and operates in the same manner above described, and the ratchet wheel 2 la is of the same form as and is secured to the totalizer wheel 20 in the same manner as above described, but in this case the ratchet wheel carries a clutch pin 15a extending through the web of the ratchet wheel with a sliding fit and secured thereto by an arcuate flat spring I05a having its ends riveted to the web of the ratchet wheel at I06Ia. In this modified construction, the transfer gear 22a is provided with a circular row of equally spaced clutch holes 18a having the same number, arrangement and purpose as the clutch holes I6 above described in the web of the ratchet wheel 2I. This modified construction operates in all respects in an equivalent manner to secure the same results as above described in connection with Fig. 15.

In Fig. '7, the cam 41 is shown engaged by a roller I'I carried by a flat bar I08 extending upwardly and forwardly on the outer surface of the partition 8 to operate the clutch shaft 85 axially. The upper portion of the bar I08 is held adjacent the partition by a shouldered screw I 09, the lower portion of said bar being held in that posi tion by being located in a small clearance space provided between the partition and the cam 41 (Fig. 14). Transverse movement of the upper portion of the bar I08 on the partition is prevented by a longitudinal slot I I0 in said bar contain ng the body portion of the screw I09 with a sliding fit, and transverse movement of the lower portion of said bar is prevented by a roller III carried by said bar entering with a free rolling fit, a slot I I2 in the part tion 8 parallel with the slot I I0. The parts described are so related that the central line of the bar I08 extends substantially through the axis of the clutch shaft 85, and that the bar is capable of only longitudinal movement towards and from said shaft 85, a spring II3 being provided having its upper end anchored in the partition 8 and encircling a lug I I formed from the partition, and pressing at its lower end against a bent lug I I5 formed from the bar I08, to at all times firmly hold the roller I01 against the cam 41. At its upper end, the bar I08 is provided with parallel flange members II6 extending perpendicularly and outwardly from said bar. through which a short pivot rod I I! extends, having end pins II8 holding it in place. The pivot rod III extends through parallel ears II9 extending outside of and adjacent the flange members I I5, which ears are formed from a lifting cam I20 having a body portion I22 parallel with and substantially spacedfroin the partition 8, and an inclined outer end portion I23 extending towards and terminating at its end closely adjacent to the partition 8. A spring I30 around the pivot rod I I1, holds the outer end of the cam I20 adjacent the partition 8 unless said cam is moved away from said partition against the action of said spring.

The inclined end portion I23 of the lifting cam is centrally slotted at I24, the width of said slot being sufl'icient to freely receive the cylindrical portion of the shaft 85 adjacent the pin 9|, but substantially less than the over-all length of 16 said pin 9|. The slot I24 extends a shortdis-v tance into the body portion I22 of the cam I20,

' where it opens into a cross slot I25 in said body portion that has a width greater than the di. ameter of the pin 9|, and a length substantially greater than the over-all length of said pin 9|, The pin 9I extends through the shaft in a direction crossing the slot, I24 perpendicularly, and parallel with the cross slot I25.

As more fully explained below, the clutching operation between the clutch pins and holes therefor, must occur during the first part of the forward stroke of each operating cycle of the handle 35. Each forward stroke of said handle is substantially degrees of movement, as is each back stroke, and as below described, full stroke mechanism is provided requiringv the handle to be moved from its back positionor position of rest, through its complete forward stroke before its back stroke can be begun, and then requiring it to be moved through its complete back stroke to its back position or position of rest thereby completing a cycle of operation, where a yielding spring holds the handle against accidental forward movement, without interferring with the next cycle of operating movement of the handle, when the same is desired.

As shown in Fig. '7, when a cycle of forward movement of the handle 35 is begun, the cam 41 begins its rotary movement in the direction of the arrow, and begins the movement of the bar I08 towards the shaft 85 by the rising surface I26 on said cam. At the start, the lifting cam I20 has the relation to the shaft 85 and pin 9I shown in Fig. 8 and the pin I5 and ratchet wheel 2| are in their unclutched posi-? tion. Rotation of the cam 41 moves the bar I08 in the direction of the arrow (Fig. 8), until the end of the rising surface I26 is under the roller I01 (Fig. 7), at which time the inclined portion I23 of the lifting cam I20 has passed completely under the pin 9I, moving the shaft 85 axially against the action of its returning spring 93 to its position effecting complete clutching between the transfer gear 22 and the ratchet wheel 2I, and at the same time placing the pin 9I on the body portion I22 of the lifting cam, but with the lifting cam not sufficiently moved under the pin III to bring the latter into alignment with the cross slot I25 (Fig. 9). This relation of the parts, effected by the rising surface I26 of the cam 4! and shown in Fig. 9, is continued for a substantial angular movement of the cam 41 by a delay surface I21 thereof,- to permit other operations below described, to be effected by rotary movement of the shaft 43 during the delay interval. The movement of the shaft 85 from its position shown in Fig. 8 to, its position shown in Fig. 9, is effected by substantially the first 30 degrees of forward movement of the handle 35 from its back position, and the delay interval represented by the delay surface I27 of the cam 47, comprises substantially the next 60 degrees of forward movement of the handle 35. At the end of the delay surface I21 of the cam 41, a second rising surface I28 of said cam engages the roller I01 and in substantially 5 degrees of angular movement of said cam, moves the lifting camv I20 enough further under the pin 9| to bring said pin into alignment with the cross slot I25, and the spring 93 at once moves the shaft 85 and parts carried thereby to their unclutched position shown in Fig. 8, at which time, however, the lifting cam 17 I20 is still in its position of maximum forward movement, which condition is continued until the end of the forward stroke of the handle 35,

' by a second delay surface I29 on the cam 41.

The following back stroke of the handle 35 produces an operation of the bar I08 that is the reverse of that described for the forward stroke, but inasmuch as it is desired that the back stroke shall have no effect on the clutching mechanism described, that result is secured as follows. The lifting cam I20 is held with its outer end adjacent the partition 8, by a spring I30. At the beginning of the back movement of the bar I08 by its spring H3, the pin BI is between the lifting cam I20 and the partition 8. As the bar I08 moves backward as indicated by the arrow in Fig. 10, the inclined end portion I23 of the lifting cam I20 engages the pin 9| and is lifted thereby against the action of the spring I30 as indicated in Fig. 10, and for continued back movement of the bar I08, the lifting cam I20 is freed from the pin 9|, and the spring I30 moves the outer end of the lifting cam to a position adjacent the partition 8 ready for its next forward movement.

In Fig. 4, the sector set-up mechanism is shown in the lower portion of said figure together with the sector resetting and transfer mechanism located in compartment I, and in the upper part of said figure the carry-over mechanism located In compartment II is illustrated.

As shown in Fig. 4, a sheet metal sector I3I is mounted for rotation on a rod I32, which extends with a sliding fit through partitions 2 to 8 inclusive but not through the end plates I and 9, in the same manner above described for the guide rod 90. As shown in Fig. 32, the sector I3I is rigidly mounted on a bushing I33 having extensions ending adjacent the partitions 2 and 3, by which the sector is maintained in the position indicated in Fig. 32, between said partitions, which bushing is a sliding fit on the rod I32. The upper circular edge of the sector is closely adjacent a corresponding index plate not shown in Fig. 4, and is provided with gear teeth I34 meshing with the teeth of a pinion I35 mounted for free rotation on a rod I35, which pinion is also in mesh with a corresponding transfer gear 22. The rod I36 extends with a sliding fit through partitions 2 to 8 inclusive, but not through the end 7 plates I and Q, in the manner above described for the'rod Q0. The pinion I35 is maintained in the position in compartment I shown in Fig. 32, by tubuiar spacers I 31 on said rod, for which position the right hand end of the pinion is substantially in line with the right hand face of the sector I3I and also with the right hand face of the transfer gear 22 when the latter is in its extreme unclutching position shown in Fig. 32. The inion I 35 has an axial length maintaining it in mesh with the transfer gear 22 when the latter is moved to its extreme clutching position shown in Fig. 9.

As shown in Fig. 4, the finger 24 is provided with an angular offset 24a in line with the teeth I34, secured to and forming a support for the arcuate indicator strip 32, and further support for the latter is provided b an angle member I38 secured to the sector I3I and also secured to said strip 32.

As shown in Fig. 4, the lower portion of the sector I3! a circular edge of smaller radius than the teeth :34, provided with V-shaped notches 139 for cooperation with a spring detent I40 rigidly secured to a supporting bar I4I, to

yieldingly hold the sector in any position it may be given in making a set-up by movement of the finger 24, the angular spacing of the notches I39 being the same as the angular spacing of the digits on the indicator strip 32 and also proportional to the angular spacing of the digits on the totalizer wheel 29 (Fig. 32) and of the clutch holes 16 in the ratchet wheel 2I. The sector and pinion construction described is duplicated in each of the compartments II to VI inclusive, and the bar I4I extends through all of said compartments and is supported for a small amount of angular movement on a rod I42 extending with a sliding fit through partitions 2 to 8 inclusive in the manner described for the rod 90. The bar MI is provided with spaced ears I43 adjacent desired ones of the partitions, which ears are provided with holes receiving the rod I42 with a sliding fit, and springs I44 are provided between the right hand edge of said bar I4! and desired ones of said partitions to press the detents I40 against the sectors with sufficient force to insure holding-the sectors effectively in positions given them in making any set-up of the fingers 24.

As shown in Figs. 3 and 21 each ratchet wheel 2| cooperates with a spring actuated detent I45 of formed sheet metal, mounted with a sliding fit on a supporting rod I45 extending with a sliding fit through holes therefor in partitions 3 to 8 inclusive in the manner above described for the rod 90, excepting that the rod I45 has its ends adjacent partition 2 and end plate 9. Each detent I45 is held in position in its compartment by a formed spacing lug I41 extending to the right from the detent and ending adjacent the partition between it and the next compartment, and a spring I48 is provided holding each detent I45 yieldingly but firmly against the corresponding ratchet wheel 2 I.

It will be observed that during movement of the fingers 24 to effect a desired keyboard setup, there is no operating engagement of any kind between the transfer gears 22 and the totalizer wheels 20 because of the open condition of the clutching devices; thus the transfer gears may be rotated to suit the operator by movement of the fingers 24 in either direction, and the setting of the fingers is accurately indicated by the digits on the indicator strips 32 that appear through the sight openings 31 in the index plates 25 (Fig. 2). Furthermore, in effecting said keyboard set-up, the clutch pins I5 carried by the transfer gears 22, are obliged to move angularly to an extent having a fixed ratio to the angular movement of the fingers 24, because of the sectors I3I being positively geared to the transfer gears 22 at all times, as a result of which when any keyboard set-up has been completed, each clutch pin I5 definitely and positively must have an angular position relatively to its 0 position, and be spaced therefrom the same number of angular units (each of which is 36 in the illustrative machine of the drawings), as represented and called for by the digit appearing in the corresponding sight opening 3|. The parts are so proportioned and adjusted, that for each holding position of each ratchet wheel 2| by its detent I 45, one of the digits on the attached totalizer wheel 20 is centered in the corresponding sight opening 33 in the casing 29, that for each holding position of each sector 43! by its detent I40, one of the digits on the attached indicator strip 32 is centered in the corresponding sight opening 3| in the corresponding index plate 25, and that'for each of said holding positions of each ratchet 19 wheel and each sector cooperating therewith, the I clutch pin I associated with said sector is in axial alignment with one of the clutch holes '56 in the cooperating ratchet wheel.

When a keyboard set-up has been effected as above described, the handle 35 is moved through its cycle of operation, and with it the main operating shaft 43. As shown in Fig. 4, the cam 49 has resting against it under the action of a spring I49, a roller I50 carried by the operating 1 arm 68 on the sector resetting shaft 64. One of the resetting arms 51 is connected with one end of the spring I49, the other end of which spring engages the tie rod I4. Each resetting arm 5'! extends to the left from the shaft 54 over and in line with a roller stud I5I carried by the sector of the arm 51, but by which an ample interval is provided so that somewhat less than that amount of forward movement of the handle 35, completes the movement of the transfer gears 22 axially into engagement with the ratchet wheels 2I and establishes the clutch relation between said transfer gears and said ratchet wheels in the manner above described in connection with Figs. '7 to inclusive. Thus at the end of the delay interval I52 of the cam 45, the transfer gears 22 are securely clutched and locked against rotation relatively to the ratchet wheels 2| and attached totalizer wheels 29,

which clutching occurs entirely by axial movement of the transfer gears 22 and this produces no tendency of any kind to displace the set-up sectors I3I from the positions in which they are 'held by the detents I40, or to displace the'totalizer wheels 26 and ratchet wheels H from the positions in which they are then held by the detents I45. Following the delay surface I52, the cam 49 is provided with a rising surface I53 of about 45 degrees in extent and of sufficient rise to move the arm 61 through an angle that will move the sector I3I from whatever its set-up position may be, back to its 0 position shown in Fig. 4, if the sector were moved from said position to effect the set-up. Because of the clutched condition referred to, of all of the transfer gears with the corresponding ratchet wheels, the resetting of the sectors I3! to their 0 position positively rotates or advances the totalizer wheels 20, each by the number of units of the set-up of the corresponding sector.

A stop rod I54 extends through partitions 2 to 8 inclusive with a sliding fit and also through a clearance opening I54a therefor in the sector I3I, said opening I54a having an angular extend such that one of its edges engages said rod when the sector is moved to its 9 position, and that an opposite edge of said opening engages said rod when the sector is moved back to its 0 position, said rod I54 being held in place as above described for the rod 90. Following the rise I53, the cam 45} is provided with a second delay surface I55 permitting continued movement of the handle 35 to the end of its forward stroke without further movement of the shaft 64 and arms 61. During the back stroke of the handle 35, the spring I49 raises the arms 61 to their original position of rest without movement of any kind of the sectors I3I, freeing said sectors for the next '20 keyboard set-up operation as far as the arms BYI? are concerned.

A stop rod I limiting movement of the cam. 49 and shaft 43 in each direction, extends with: a sliding fit through partitions 2 to 8 inclusive: and is held in place as described for the rod 90;. After the transfer operation of the set-up: amount from the sectors I3I to the totalizer wheels 2fi'effected by returning the sectors I3I. to' their 0 positions by the rise I53 of the cam 49,. and while the arms 6'! are still in their positions: holding the sectors I3I in their 0 positions by' the action of the delay surface I55, when about; 5 of said delay surface has passed under the: roller I55, the second rise I28 of the cam 41 has moved the bar I58 sufficiently to release the pin SI from the lifting cam I25, thus insuring that the sectors I3I shall be fully returned to their Q positions before the clutching mechanism. between the transfer gears 22 and the ratchet wheels 2I is released and the transfer gears 22. are moved to their positions indicated in Fig. 8,. It will be observed that during the resetting of. the sectors I3I to their 0 positions, conditions"- may readily develop where all of the sectors must be simultaneously reset against the resistance of all of the sector detents I49 and all of the totalizer detents I45, thereby placing a heavy load on the handle 35, unless means are provided to decrease that load. In view' of the transfer gears 22 being positively clutched to the: ratchet wheels 2| during the resetting of the sectors I31, the totalizer detents I45 can be relied upon during that interval to not only prevent accidental displacement of the totalizer wheels 25, but also of the sectors I3I, thus permitting substantially decreasing the handle load represented by the sector detents I45, as illustrated in Figs. 5 and 6. i i

As shown in Fig. 5, the cam 48 in the compartment III has resting against it a roller I51 carried by the right hand end of a horizontally disposed fiat bar I58 pivotally connected at its left hand end at I59 with the mid-portion of a lever I60 pivotally connected at its upper end at IGI with the partition 5 against which said bar I58 rests, being held fiatwise against said partition in part by having its right hand end disposed between the cam 48 and said partition, and in part by its pivotal connection I59. The right hand portion of the bar is restrained againstappreciable vertical movement by a roller IE2 carried by said bar, engaging with a rolling fit a horizontal slot I53 in the partition 5. The lever IBil is disposed vertically above the right hand end of the sector detent I40 in compartment III, and has pivotally connected with its lower end at I54, a pawl I55 engaging a ratchet wheelIGS pivotally mounted by means of a stud I61, on the partition 5, the lower edge of said ratchet wheel I resting against the upper surface of the right hand edge of the bar I4'I supporting all of the sector detents I40, to restrain upper movement of said right hand edge under the action of the spring or springs I44. The teeth of the ratchet wheel I65 are sufficiently large and deep, and the parts are so proportioned and positioned that when said right hand edge is between two adjacent ones of said teeth and restingagainst the bottom of the notch between them as shown in Fig. c, said right hand edge is held in its uppermost position by the spring or springs I44, which have a strength sufiiciently greater than all of the spring detents I40 to maintain that position of said right hand edge against the operation When the amount against the action of the spring or springs M4, to nearly or quite relieve the sector I3I of the holding action of the spring detent I48 as shown in Fig. 6. A spring I68 between 1 the pawl I65 and the bar I58 holds the pawl in engagement with the ratchet wheel I66, and a spring I69 coiled around a post I18 extending from the partition 5, and with its upper end anchored in an opening in said partition and i resting at its lower end against a bent lug I1I formed from the bar I58, holds the roller I51 firmly against the cam 48.

The first part of the operating surface of the cam 48 is a delay surface I12 of about degrees in extent. This holds the bar I58 and ratchet wheel I66 in the positions shown in Fig. 5, and during the interval the cam 41 has sufficiently moved the shaft 85 so that there is substantial clutching engagement between the clutch pins 15 and the ratchet wheels 2I and control against acc dental movement of the sectors I3I has been established by the pawls I45, before any weakening of the applied pressure of the spring detents I40 takes place; the delay interval I12 of the cam 48 is followed by a rise I13 of about degrees of angular extent, that moves the bar I4! from the position shown in Fig. 5 to the position shown in Fig. 6, thereby nearly or qu te freeing the sectors I3I from restraint by the detents I as above described, the clutching operation between the pins 15 and ratchet wheels 2I being completed during the first part of said rise, and

the movement of the detents I40 to the positions indicated in Fig. 6 being completed at the end of said rise I13; following the rise I13, the cam 48 is provided with a second delay surface I14 of substantially degrees in extent, holding the detents I 40 in the position shown in Fig. 5 during the entire resetting movement of the sectors 'I3I above described as effected by the arms 61, during which entire resetting movement of the 1 arms 61, the pins 15 and ratchet wheels H are positions shown in Fig. 6 to the positions shown in Fig. 5; the second rise I15 of the cam 48 is followed by a third delay surface I15 to complete the forward movement of the cam 48. It will be noted that the back rotation of the cam 41 by the back stroke of the handle 35. produces no movement whatver of the shaft 85 from its previously established unclutching position, serving only to effect the movement of the bar I88 to its in tial position by the action of the spring II 3; that the back rotation of the cam 48 1? produces no effect whatever on the detents I48,

"serving only to effect the movement of the bar I58 'to its initial position by the action of the spring I68, thereby moving the pawl I to a new positon of operative engagement with the ratchet wheel I66, the latter being held against back rotation by the bar M! then serving as a holding pawl for said ratchet wheel; and that the back rotation of the cam 48 produces no effect whatever on the sectors I3I, excepting to free nthem'for effecting the next keyboardiset' up,isaid back rotation serving onlyto raise the arms 61 to their initial positions away from the studs I5I, by the action of the spring I49.

As shown in Fig. 31, the full stroke plate 58 (Figs. 3 and 14), is provided with an upper circular edge having closely spaced shallow notches I11 therein to engage a spring actuated pawl I18 pivota-lly supported on a stud I16 extending outwardly from the end plate I. The plate 58 is shown with its upper portion in its rear or initial position, further rearward movement thereof being prevented by the engagement of a radial edge I88 of the plate 58 with the stop rod I55, for which rod a recess is provided'in said plate 58 so that an opposite radial edge I8I of said plate 58 engages said rod at the end of the forward stroke of the operating handle 35. The upper end of the pawl I18 is connected by a spring I82 with a stud I 83 extending from the plate I, so that when said pawl is free from the notched circular edge of the plate 58, said pawl is held in a radial line through the axis'of rotation of said plate, by the tension of said spring. The pawl I18 is mounted on the end plate I so inner end is somewhat nearer the axis of rotation of the plate 58 than are the notches I11, and said inner end is provided with two spaced holding edges I84 and I85. As a result of the con truction described, when the handle 35 is moved through the forward stroke of its operating cycle, the pawl I18 is swung to an inclined position with its back edge I84 in engagement with the notches I11, thereby permitting only forward movement of the handle 35 until the rear edge of the notched portion reaches the pawl. The notched portion of the plate 56 is of somewhat smaller angular extent than the angular spacing of the edges I88 and I 8I from each other, as a result of which when. at the end of the forward stroke of the handle 35, the edge I8! engages the stop rod !55, the pawl I13 clears the rear edge of the notched portion of the plate 58 and moves to its radial position permitting the back stroke of the handle 35 to begin, which inclines the pawl in an opposite direction to its first inclination and engages the edge I85 with the notches 11. thereby permitting only back movement of the handle 35 until the edge I88 engages the stop rod 558, which places the handle 35 in its back position of rest and clears the pawl I18 for movement to its radial position ready for the next cycle of o eration. A spring I86 around the connector 54 (Fig. 3), and having its ends engaging the cam 49 and partition 2, moves the shaft .3 and handle 35 through their back rotation and stroke, the strength of said spring being sufficient to positively overcome any forces of resistance to said back rotation and stroke that e exerted on said shaft by the parts of the machine.

The carry-over mechanism of the machine is shown in Figs 3, 4 and 21 to 25 inclusive, which mechanism includes in each of the compartments II to VI inclusive an operating slide 26, a trigger latch 2! and a timing latch 28, and in addition, a slide resetting lever I8! (Fig. 4), for moving the a sociated slide 25 to its extreme rear position at the beginning of each cycle of operation of the handle 35. 7

As shown in the upper part of Fig. 4, for the carrr-over mechanism in compartment II, the slide 26 is supported in a n arly horizontal position by front and rear parallel rods 188 and I88 each extending with a sliding fit through par- 1 rod I46.

titions' etc 8 inclusive andheld in place as above described for the rod I46. is preferably of sheet metal formed into a U- Each of the slides'26 shape opening upwardly with the legs of the I U parallel and forming the side walls of the =slide, which are provided with slots I90 and I? receiving the rods I88 and I89 with a sliding fit j and thereby affording stable support for the slide. The slots I 98 and I9I are of a length permitting the maximum required longitudinal movement of the slide, and one or both of the rods I88 and I89 engage the rear ends of their said slots when the slide is moved to its extreme forward position, thereby limiting said forward movement of the slide. A spring I92 extends in the slide 25 from the rod I88 to the rear portion of the slide where it is attached to said slide to move the slide forwardly when it is released from I the holding engagement of the latches 21 and 28.

The front end of the slide has pivotally connected therewith at I93, a spring actuated pawl I94 the resetting lever I8! is preferably formed from sheet metal to have a U-shaped mounting portion through the parallel side walls of which a supporting rod I95 extends with a sliding fit, which rod also extends with a sliding fit through the partitions 3 to 8 inclusive and is retained therein in the manner described above for the One side wall of the supporting portion of the lever I8! is extended upwardly and adjacent a side wall of the slide 26 where it is longitudinally slotted at I95 to receive with a sliding fit the projecting end portion of a stud I9! extending through and rigidly secured to the side walls of the slide. Said side wall of the lever I8? is also extended below its mounting portion and has pivotally connected therewith at I98 a spring actuated pawl I99 in the path of movement of the bent end portion 58a of the arm 48 when the latter is moved by operation of the handle 35.

The arm 46 is adjacent a downwardly extending setting arm 28a of the timing latch 28 in the path of movement of a lug 45?) extending laterally from the arm 46 and so related angularly to thearm 28a that the last 19 degrees of each back stroke of the handle 35 will move the latch to its slide-releasing position shown in Fig. 4 against the action of a spring 281), and that the first 10 degrees of in its extreme forward position, and a further forward movement of the arm 46 after releasing the latch 28, of about 10 degrees is required to move the slide 26 to its extreme rear position ready for the next carry-over operation. This accomplishes three things: first, it delays the carry-over operation in connection with each cycle of operation of the handle35,;untiltheilast few degrees of each cycle. and until after-all other operations effected by the handle '35 are completed; second, it insures that the timing latch 28 shall be in a position to hold the'slide 25 in its reset or rear position when by theresetting operation, the slide reaches that; position; and third, it insures that the slide 126 shall reach its reset position well in advance of "anything occurring in the cycle of operation of the handle 35, that could require any movement or conditioning of the slide incident tostoring a carry-over operation for release later in the same cycle of operation. l

After the slide 25 is moved to its reset position by operation of the lever I81 as described, and the .handle 35 has completed its forward stroke and is in its back stroke, when the bent end 48a reaches the lower end of the lever I8'I, for reasons pointed out below, the point of the pawl I99 is to a small extent in the path'of said ent end, but return movement of said bent end continues without interruption or restraint, because of said pawl turning on its pivot I98 against the action of its spring until it clears the bent end 46a, when it is returned by its spring to its operating position shown in Fig.

The trigger latch 2'! shown in Fig. 4 is' preferably formed from sheet metal into a U-shaped structure opening downwardly and pivotally supported by a rod 298 extending with a sliding" fit through its side walls and also through partitions 3 to 8 inclusive and held therein in the manner above described for the rod MB. The latch 21 is in part in a higher position than the slidei28, but to one side of said slide, with the ad acent side walls of said latch and slide overlapping each other, the combined width of said latch and slide being a free fit between the partitions 3 and 4, the latch being thereby held adjacent partition 3 and the slide being held adjacent partition 4 (Fig. 3). The lower'portion of the side wall of the latch 2! adjacent the slid'e'26, is provided at its front end with a lug 20I extending for the lowermost position of said latch,

into the path of movement of the slide 28, whereby for said lowermost position, said lug 2M engages the upper portion of the end of the adjacent side wall of the slide with the slide'in'its rearmost or reset position, and holds the slide in that position against the action of the spring I92. The side wall of the latch 21 near the adjacent partition of the compartment, is provided with a forwardly extending arm 2G2 having at its front end a laterally extending lug 293 for raising the latch to release the slide from the lug 29!, in the manner below described.

Figs. 21, 22 and 2-3 show the slide 26',"the trigger latch 21 and the timing latch 28 in the compartment II. in their different positions of operation. In Fig. 21, the slide 26 is in its rear or reset position, with the lug 28I in its position to prevent forward movement of the slide 26 and with a hook 280 on the timing latch 28 in an opening therefor in the bottom of the rear end portion of the slide, but with an appreciable clearance space between the hook and the rear edge of said opening. As shown in this figure, the slide resetting arm 49 is moving forwardly but has not quite completed its slide resetting movement, which resetting movement has, however, progressed sufficiently so that the latch 21 under the action of its spring 21a, has moved downwardly to its position holding the slide 26 against forward movement. The remaining small amount of forward movement of the arm required to clear the arm from the resetting lever I81, moves the slide 20 rearwardly a small amount from the position shown in Fig. 21 thereby providing a small clearance between the front end of the slide and the holding lug 20! on the latch 21, thereby permitting the latch to move quickly, freely and accurately to its slide holding position, even for rapid movement of the operating handle 35. When the arm 40 has passed the lever I81, the spring I92 moves the slide 26 to the position shown in Fig. 21 against the lug MI, and also extends the lower end of the lever I81 slightly into the path of return movement of the bent end 46a of the arm 46, which in part accounts for providing the spring actuated pawl I99 on the lower end of the lever I81, to permit free. return movement of the arm 46 and to avoid the possibility of damage to the parts which might otherwise occur during said return movement. cycle of operation of the handle 35 after resetting the slide 26, the operation of the slide 28 is entirely controlled by the latches 21 and 23. It will be noted that in Fig. 21, the spring actuat-v ed pawl I94 is in a position spacing its forward end a substantial distance to the rear of the lower teeth of the ratchet wheel 2| attached to the totalizer wheel 20. It will also be noted that the spring actuated detent I 45 is provided with a wedge-shaped pointed end I45a having widely diverging sides, so that if any operation of theratchet wheel 2| moves one of its teeth under and past the pointed end 45a, the detent spring I48 will at once move the pointed end to a bottoming position between corresponding ones of said teeth and establish a centered relation of one of the digits on the totalizer wheel 20 relatively to the corresponding sight opening 33in the casing 29.

Fig. 22 shows the parts illustrated in Fig. 21. in the relative positions they assume when the arm. 202:is raised by movement of the totalizer wheel 20.0f next. lower order from its 9 to its 0;position. The relation of the parts shown in Fig. 22,.is maintained until just before the end of .thecycle of operation of the handle, illustrated by Figs. 21, 22 and 23.

For the position of the parts shown in Fig. 22, the slide 26 has moved forward a small amount, until the hook 290 engages the rear edge of the slideopening containing it, and for this position of the slide, the lug 20I now released from the lifting, mechanism of the totalizer wheel 20 of next lower order, has dropped and is resting upon an upper edge of the slide 26 with the slide moved forwardly an amount suflicient to prevent engagement between said lug and the front end of the slide. The pawl I94 is now. forward a small amount from its positon shown in Fig. 21, but not enough so to engage the teeth of the ratchet wheel 2|. The lever I8! is also moved a small amount around to the left on its supporting rod I95 which is a further reason for providing the lower end of the lever with the spring actuated pawl I99. The slide is now under the soie control of the timing latch 28, and remains so until just before the end of the cycle of operation of the handle under consideration.

In Fig. 23 the position of the parts is shown at the end of the cycle of operation of the handle 35. The timing latch 28 is in its releasing position. by engagement with. the .lug 46b and the slide.26.is in its extreme forward position by the action. of .its spring I92. In moving to the posi- During the remainder of the tion shown in Fig.-23,-'the pawl I94 has engaged the tooth of the ratchet wheel 2| shown in line with and in front of itin Figs. 21 and 22 and handle, and during about the second 10 degrees of the forward stroke of said next cycle, all of the slides that are in their forward or carry-over positions, are reset and moved to their extreme rear positions shown in Fig. 21, by the operation of the bent ends 4811" of the arms 48 carried by the main shaft 43. Each of compartments II to VI inc .usive is provided with carry-over mechanism identical with that shown and described in connection with Figs. 21, 22 and 23, and having "1e same mode of operation.

In Figs. 24, 25 and 26, the means employed to operate one of the trigger latches 21, is shown In order to-avoid confusion as to the planes of sectioning shown in Fig. 3, the carry-over mechanism shown in Figs. 24, 25 and 26 is that located in compartment III, but with the same force and effect as though the carry-over mechanism of compartment 11 were shown in said figures.

In Fig. 24:, the lug 203 on the operating arm 252 of the trigger latch 21, is shown extending into the path of cam i 04-II through a clearance opening 204 in the adjacent partition 4 and resting on the lower edge of said opening, which is the lowermost position of the latch 21 and arm 202 and which determines the extent that the lug 20! initially holding the slide 26 against forward movementvertically overlaps the end of said slide. The cam I04II of totalizer wheel 20--II, is shown in the position it has when the L 9 digit on the totalizer wheel 20II is displayed in the corresponding s ght opening 33 in the casing 29. When the totalizer wheel 20II is advanced to its 0 position, the cam l04-II is advanced to the position shown in Fig. 26 and during the advance of said cam, it raises.

the lug 203 to its uppermost position as shown in Fig. 25 at the mid-position of said advance move ment, and at the end of said advance movement the cam has passed under and cleared said lug,

A which permits the arm 202 and latch 2'! todrop than that requiredto move the lug 2JI upwards to its slide releasing position, which permts the small initial forward movement of the slide 26 above described, to take place free from any holding or frictional resistance of the latch 21.

and insures that when the latch is freed from the cam I04-II,' it will drop on an upper edge of the slide 26, since said slide is free to move immediately and without retraint, when the hold-- ing lug MI is lifted from engagement with it. It will also be noted that the same result is secured as above described whether the advance movement of the totalizer wheel 20-11 begins 

